Sluice gate



Oct. 10, 1967 s. RAKCEVIC SLUICE GATE 5 Sheets-Sheet i Filed March 20, 1964 Oct. 10, 1967 s. RAKcEVIc 3,345,823

' SLUICE GATE} v I Filed March 20, 1964 5 Sheets-Sheet? FIG.2. 11 30 Avwwro? 541 0 RA/(aEV/c fir-r Oct. 10, 1967 5, RAKCEVlc 3,345,823

SLUICE GATE Filed March 20, 1964 3 Sheets-Sheet 5' 83M PJM United States Patent 3,345,823 SLUECE GATE Savo' Rakcevic,Ljubljana, Yugoslavia, assignor to Titovi Zovodi Litostroj, Ljubljana, Yugoslavia, a Yugoslav company Filed Mar. 20, 1964, Ser. No. 353,377 (Ilairns priority, application Yugoslavia, Mar. 29, 1963,

8 Claims. (CI. 61-24) The invention relates to a sluice gate for liquids, particularly for large rates of flow, such as occur in lowpressure hydroelectric power stations.

Various known types of closure devices are used for closing sluiceways. For example, in the case of Weirs the individual sections are shut off by sluices of relatively large dimensions, which are moved in agenerally vertical direction by means of a suitable Winch. Weirs with sluices, valves or the like of known construction also have the disadvantage that they are very heavy and can be opened or closed only slowly as a result of the large distances through which the sluices have to be moved.

The invention relates to a novel closure device which does not have the above-mentioned disadvantages and which can also be used for controlling the rate of flow of the liquid and permits rapid closing and opening. Moreover, it is suitable for use in conjunction with other closure and/ or control devices.

The sluice gate for liquids according to the invention is provided with a larger number of parallel closure members which are arranged to pivot about their eccentric axes and can be moved simultaneously by a setting device controlled by a servomotor. The closure members are so arranged that they are subjected to the pressure of the liquid. On decrease of the pressure of the control medium, e.g. the control liquid, by a chosen amount, this hydraulic pressure can cause the closure members to rotate and can move the servomotor pistons by means of the setting device. These pistons force the control medium from the servomotors. The displaced control medium can be supplied to the servomotors of further closure and/ or control devices for simultaneous operation, preferably in the opposite direction. A pressure-regulating valve for regulating the moment and speed of adjustment of the closure members is preferably provided in the conduits or the control medium, e.g. in the distributing slide valve of the control medium.

The closure members can be arranged in groups in such manner that adjacent groups open in opposite directions and thus deflect the efliuent liquid in different directions which partially intersect. In this manner, the energy of the eflluent liquid is used in the liquid itself In the case of hydraulic machines, e.g. water turbines, the sluice gate can be arranged in the supply or outlet conduit, or in the channel or pipe which is connected to the spiral of the housing of the hydraulic machine. The sluice gate of the present invention can also be connected with the guide wheel of the hydraulic machine, so that it opens when the guide wheel closes. This is achieved by arranging for the pistons of the. closure device servomotors, under the action of the torque exerted on the setting device by the liquid pressure, to displace the control medium on decrease of its pressure from the closure device servomotors to the guide wheel servomotors of the hydraulic machine.

Finally, for securing the closure member setting device and thus the closure device itself in the open or closed position or, if required, in any intermediate position, mechanical, electromagnetic or hydraulic securing means can be provided in known manner and, if necessary, these securing means can be reciprocally connected with other securing devices, e.g. for the guide wheel of the hydraulic machines.

Embodiments of the sluice gate according to the present invention are described in greater detail below in conjunction with the accompanying drawings, in which:

FIG. 1 shows diagrammatically one form of sluice gate for a water turbine;

FIG. 2 is a front elevation of the individual closure members; 1

FIGS. 3 and 4 are two further front elevations of the closure members of the sluice gate;

FIG. 5 shows diagrammatically a further embodiment of the closure device.

The sluice gate 1 according to FIG. 1 comprises six vertical closure members 2 whose spindles 3 are rotatably mounted within the frame 4 of the closure and/ or control device 1, e.g. in the lateral outlet from a turbine spiral. Each closure member 2 is connected with a setting device by means of a control rod 6 and associated levers 5 and 5'. The end of the lever 5 of the setting device is secured to the closure member 2 or its spindle 3 and the end of the lever 5 is secured to the control rod 6. Both levers '5, 5 of the setting device are movably connected together.

The pistons 7 of servomotors 8 for operating the closure.

and/ or control device are connected with the control rod 6. This connection with the closure members 2 is arranged so. that, on displacement of the pistons 7 of the servomotors 8, all the closure members 2 pivot through the same angle. The closure members 2 and the setting device are arranged in two adjacent groups, so that one half of the closure members 2 pivot in one direction and the other half in the opposite direction. Therefore, when the closing device is open or partially open, the effluent water flows in intersecting directions, as indicated by the arrows.

The spindles 3 of the closure members are arranged eccentrically with respect to the profile of the individual closure members 2. Consequently, when the closure members are open or partially open, the hydraulic pressure of the dammed liquid produces a moment of rotation which acts in the opening direction of the closure members 2. The moment of rotation of the setting device 5, 5', 6 acts in the opposite direction to the first-mentioned moment of rotation under the influence of the servomotors 8. As a result, the closure members 2 open only on decrease of the pressure of the control medium in the servomotors 8. By suitable choice of the pivot points of the positions of the spindles 3, the hydraulic pressure of the dammed liquid can be caused to apply a corresponding force to the closure members 2, which force can be transferred to other control devices by means of a suitable hydraulic device as will be explained in more detail below.

For securing the setting device or the sluice gate 1 with the closure members 2 in the open or closed position, securing means 9 are provided which act under the influence of mechanical, electromagnetic or hydraulic control members.

The cylinders of the servomotors 8 of the closure and/ or control device are connected by means of conduits 10 with the servomotors 11 of the guide wheel 12 of the turbine 13 Whose rotor is mounted on a shaft 14. In addition, the conduit 10 is connected with a pump 16 for the control medium by means of a conduit 15. A pressureregulating valve 17 in parallel with a one-way bypass valve 18 is arranged in this conduit. A control valve 19, a pressure-responsive switch 20 and an electromagnetic slide valve 21 are also provided in the supply conduit 15. This slide valve 21 is connected at one side with the servomotors 11 of the guide wheel 12 by a conduit 22 and at the other side with a reservoir 24 by a conduit 23. A control member 25 actuates the slide valve 21. In addition, securing means 26 are provided for securing the guide wheel 12 in the closed position of the turbine blades.

FIG. 2 shows the arrangement of the device described in conjunction with FIG. 1. The closure device 1 is pro- 3 vided at the end of a pipe 27 which is connected to the spiral 28 of the turbine 13, as an approximately co-axial extension of the supply pipe 29. The discharge conduit 30 is constructed in the usual manner.

The sluice gate according to FIG. 1 operates in the following manner:

When the turbine is stationary, the pump 16 for the control medium maintains a constant pressure of the control medium in the conduits and the servomotors 8, 11 by means of the pressure regulating valve 17. The pistons 7 of the servomotors 8 are located in the positions in which the closure device 1 is closed and the turbine blades of the guide wheel 12 are open. If the load of the plant slowly decreases, the rate of fiow of the effluent water must be reduced by rotating the blades of the guide wheel 12. Closing of the guide wheel takes care of the turbine regulator in that the control medium is displaced from the servomotors 11 of the guide wheel 12 to the reservoir 24 through the slide valve 21. The pump 1:: can supply the control medium through the pressure-regulating valve 17 and the conduits 10 to the servomotors 8 and 11 in such an amount that the pressure of the control medium remains constant in the conduits 10, the servomotors 8 and at the closed side of the servomotors 11 and therefore the closure device 1 does not open. This means that adjustment of the pressure-regulating valve 17 determines the reduced rate of flow through the guide wheel 12 of the turbine 13 at which the closure device 1 begins to open.

On rapid closing of the guide wheel 12 of the turbine 13, e.g. on rapid loading of the plant, the lateral outlet should be opened and the closure device 1 opened at the same time as the blades of the guide wheel 12 close. Under the influence of the control member 25, a predetermined quantity of the control medium is displaced from the servomotors 11 of the guide wheel to the reservoir 24 through the slide valve 21 and the conduit 23. However, a suflicient quantity of the control medium under pressure cannot flow through the pressure-regulating valve 17 and consequently the pressure of the control medium in the conduits 10 and the servomotors 8 and 11 diminishes. The hydraulic pressure of the water therefore pivots the eccentrically-positioned closure members 2 and the closure device 1 allows water to flow through. As a result, the pistons 7 of the servomotors 8 force the control medium out of the servomotors 8 of the closure device and into the servomotors 11 of the guide wheel 12, thus closing the blades of the guide wheel 12.

The rate of flow of the water through the closure device 1 is dependent upon the amount of control medium forced out of the servomotors 8. This displaced control medium causes simultaneous opening of the closure device 1 and closing of the guide wheel 12, so that the rate of flow in the supply and withdrawal system remains constant. The volume of the servomotors 8 should therefore be at least approximately equal to the volume of the guide wheel servomotors 11. As a result, the closure device 1 allows water to flow through in an amount which corresponds to the reduced flow of water through the turbine 13.

As soon as the control medium is no longer flowing through the conduit 22, the closing movement of the blades of the guide wheel 12 and the opening movement of the closure device 1 are completed. The pressure of the control medium in the conduits 10' and in the cylinders of the servomotors 8 and 11 is then smaller than the pressure of the control medium in the supply conduit 15. Consequently, the control medium flows slowly through the pressure-regulating valve 17 to the servomotors 8 and its pressure rises. The servomotors 8 slowly close the closure device 1. The closing velocity is dependent upon the pressure-regulating valve 17. The pistons of the servomotors 11 are stationary, as the control medium cannot flow from the cylinders of the servomotors 11 because the slide valve 21 is closed.

Opening of the blades of the guide wheel 12, e.g. on increase of the load or on starting the turbine, does not cause any decrease of the pressure in the servomotors 8 and 11 and the conduits 10. The sluice gate 1 thus remains closed. The control medium flows from the servomotors 11 through the conduits 10, the pressure-regulating and one-way valves 17 and 18 and the conduit 15 to the slide valve 21 and the conduit 22 and so back to the other sides of the pistons of the same servomotors 11.

FIGS. 3 and 4 show two further arrangements of the closure device which has been described. FIG. 3 shows a closure device 1 incorporated in the supply conduit 29 to the spiral 28 of the turbine and FIG. 4- shows a closure device 1 incorporated in the withdrawal conduit 30 of the turbine.

The choice of location of the sluice gate depends upon the intended use. For example, FIG. 5 shows a closure device 1 in which the spindles 3 of the closure members 2 are arranged eccentrically with respect to the profile of the individual closure members 2, so that the hydraulic pressure of the dammed liquid causes a moment of rotation which acts in the closing direction of the closure members 2. In normal operation, the control medium under pressure in the servomotors 8 counteracts this moment of rotation. The pistons 7 of the servomotors 8 are so positioned that they maintain the closure members 2 in the open position by means of the setting device 5, 5', 6.

The closure device 1 described operates quickly and automatically. The servomotors 8 are interconnected by means of the conduit 10 and are also associated with the pump 16 for the control medium and with the safety valve 19 by means of the pressure-regulating valve 17. A distributing slide valve 31 which is controlled by a suitable control member 32 is connected with the conduit 10. In the case illustrated, the closing velocity of the closure device 1 is dependent upon the pressure-regulating valves 33 in the piston of the distributing slide valve 31. These pressure-regulating valves determine the flow velocity of the control medium to the reservoir 24 through a conduit which is not shown in the drawing. Further securing means 9 are provided for securing the closure device 1 in either of its two extreme positions.

In normal operation, the oil pump 17 maintains the required oil pressure in the chambers of servomotors 8 and the flaps can therefore maintain their open position. If required, the valve 32 moves under the influence of the magnet switch 26, and opens the exit of the chambers of servomotors 8 through the conduit 10 and throttle member 33 of the slide valve 32 in the oil sump 25.

Closing of the sluice gate is rendered possible by the drop of oil pressure in the chambers of the servomotors 8, and this drop of oil pressure appears because the outlet size of the throttle member 33 is larger than that of the throttling member 18. On repeated opening of the sluice gate, the oil leaves the chambers through the throttle member 33 which remains closed by means of the magnet 26, which makes the piston valve 32 move downwards; thereafter the pressure oil is admitted through the throttling member 18 and conduit 10, to pass into the chambers of sluice gate servomotors 8, and the sluice gate opens.

I claim:

1. A sluice gate for preventing waving in liquid at a high flow rate, the gate comprising a plurality of parallel flaps, a frame, the flaps being pivoted on the frame and having their axes in the same plane, the flaps being movable simultaneously between a gate-open and gate-closed position, pairs of levers, a regulating rod, each pair of levers having a common free pivot, the ends remote from the free pivot being connected one to the flap adjacent its axis and the other to the regulating rod, and a control means, the regulating rod being axially movable in response to movement of the control means to cause the flaps of one part of the sluice gate to open in one direction and those of another part to do likewise simultaneously in the opposite direction and be thus adapted to direct liquid in different directions which partially intersect.

2. A sluice gate as recited in claim 1, and hydraulic means for moving the regulating rod, comprising at least two servomotors, one disposed at either end of the regulating rod.

3. A sluice gate according to claim 1, and a hydraulic circuit for moving the flaps, and a safety valve in the hydraulic circuit.

4. A sluice gate as recited in claim 1, and a hydraulic circuit, the control means comprising an electrically operated slide reel valve and a throttle member in the hydraulic circuit.

5. A sluice gate as recited in claim 4, and means driven by the hydraulic circuit for moving the regulating rod, comprising at least two servomotors, one disposed at either end of the regulating rod.

6. A sluice gate as recited in claim 1, and turbine apparatus having turbine vanes, and means responsive to a partial opening of the sluice gate to eifect a simultaneous corresponding closing of the turbine vanes.

7. A sluice gate as recited in claim 6, in which the lastnamed means comprises a servomotor of the sluice gate hydraulically connected to regulators for said turbine apparatus having servomotors controlling the turbine vanes and disposed in the same hydraulic circuit as said sluice gate servomotor.

8. A sluice gate as recited in claim 7, the sluice gate servomotor having a cylinder having a liquid capacity greater than that of the turbine regulators thus permitting the turbine vanes to close although no further admission of liquid to said hydraulic circuit is effected.

References Cited UNITED STATES PATENTS 4,922X 11/ 1827 Seymour 61-24 2,101,973 12/1937 Becher 61-22 2,681,660 6/1954 Avery et al. 137-25 2,918,077 12/1959 Jack 16-24 X 2,938,527 5/ 1960 Nichols 137-25 3,007,675 11/1961 Suss 137-212 X 3,063,460 11/ 1962 Krauss 137-25 FOREIGN PATENTS 322,606 10/ 1902 France.

EARL I. WITMER, Primary Examiner. 

1. A SLUICE GATE PREVENTING WAVING IN LIQUID AT A HIGH FLOW RATE, THE GATE COMPRISING A PLURALITY OF A PARALLEL FLAPS, A FRAME, THE FLAPS BEING PIVOTEDD ON THE FRAME AND HAVING THEIR AXES IN THE SAME PLANE, THE FLAPS BEING MOVABLE SIMULTANEOUSLY BETWEEN A GATE-OPEN AND GATE-CLOSED POSITION, PAIRS OF LEVERS, REGULATING ROD, EACH PAIR OF LEVERS HAVING A COMMON FREE PIVOT, THE ENDS REMOTE FROM THE FREE PIVOT BEING CONECTED ONE TO THE FLAP ADJACENT ITS AXIS AND THE OTHER TO THE REGULATING ROD, AND A CONTROL MEANS, THE REGULATING ROD BEING AXIALLY MOVABLE 